High-elastic heavy-load coupler for mill and design method

Abstract

The invention discloses a high-elastic heavy-load coupler for a mill and a design method. The high-elastic heavy-load coupler for the mill comprises an inner gear ring, an outer gear ring, an outer gear ring, an inner gear ring, an outer gear ring and an outer gear ring, the inner gear ring is provided with inner teeth, and a tooth groove is formed between every two inner teeth; outer teeth are arranged on the outer gear ring, the outer gear ring is arranged in the inner gear ring in a sleeving mode, and one outer tooth is arranged in one tooth groove; one elastomer group is arranged between one outer tooth and one inner tooth, the elastomer group at least comprises a first hardness elastomer group and a second hardness elastomer group, and the hardness of the first hardness elastomer group is greater than that of the second hardness elastomer group. The elastic body has the buffering performance with the soft hardness and also has the hard torque transmission effect, when equipment is started, the elastic body with the low hardness is firstly stressed and compressed, and the good buffering and damping effect is provided; when the elastic body is compressed to a certain amount, the elastic body with high hardness begins to contact and bear force, and therefore large torque is transmitted.

Description

Technical Field

[0001] The invention relates to the technical field of couplings, and in particular to a high-elasticity and heavy-load coupling for a mill and a design method for the high-elasticity and heavy-load coupling for a mill. Background Art

[0002] Couplings can be divided into flexible couplings and rigid couplings according to whether they have the ability to compensate for the misalignment of the two connected shafts. Flexible couplings have compensation capabilities. Among flexible couplings, according to whether the couplings have elastic elements, they can be divided into flexible couplings with elastic elements and flexible couplings without elastic elements.

[0003] In a flexible coupling with elastic elements, the centering error of the two connected shafts is compensated by the deformation of the elastic elements. Of course, the torque also needs to be transmitted through the elastic elements, which puts higher requirements on the elastic elements, that is, they need to achieve both rigidity and flexibility, with sufficient rigidity to transmit torque and sufficient flexibility to provide buffering and shock absorption.

[0004] This leads to a contradiction. The existing technical solutions generally use non-metallic elastomers as elastic parts. However, in order to ensure that the coupling can transmit a sufficiently large torque, the hardness of the non-metallic elastic parts is generally high, and the final buffering and shock absorption effect is average (that is, the hardness of the non-metallic elastic parts makes it impossible to provide an appropriate buffering effect). In addition, the hubs at the left and right ends of the coupling are relatively fixed, which determines that its axial error compensation ability can only be within a very small range.

[0005] Therefore, those skilled in the art provide a high-elasticity and heavy-duty coupling for a grinding mill to solve the problems raised in the above background technology. Summary of the invention

[0006] The purpose of the present invention is to solve the shortcomings in the prior art and to propose a high-elasticity and heavy-load coupling for a grinding machine.

[0007] To achieve the above object, the present invention provides the following technical solutions:

[0008] A high-elasticity and heavy-load coupling for a mill, comprising:

[0009] An inner gear ring, wherein the inner gear ring is provided with inner teeth extending toward the center direction of the inner gear ring, and a tooth groove is formed between every two inner teeth;

[0010] An outer gear ring, wherein the outer gear ring is provided with outer teeth extending away from the center direction of the outer gear ring, the outer gear ring is sleeved inside the inner gear ring, and one of the outer teeth is arranged in one tooth groove;

[0011] An elastomer group, wherein the number of the elastomer groups is multiple, one of the elastomer groups is arranged between one of the outer teeth and one of the inner teeth, and the elastomer group includes at least a first hardness elastomer group and a second hardness elastomer group, and the hardness of the first hardness elastomer group is greater than the hardness of the second hardness elastomer group; wherein,

[0012] When the mill is started with the high-elasticity heavy-load coupling, the second hardness elastic body group is first subjected to force. After the second hardness elastic body group is squeezed and deformed by the force, the first hardness elastic body group begins to be subjected to force.

[0013] Optionally, each tooth groove is divided into a first volume tooth groove and a second volume tooth groove by the external teeth located in the tooth groove, the first hardness elastomer group is accommodated in the first volume tooth groove, and the second hardness elastomer group is accommodated in the second volume tooth groove.

[0014] Optionally, each of the first hardness elastic body groups includes a first hardness elastic body;

[0015] Each of the second hardness elastomer groups includes a second hardness elastomer.

[0016] Optionally, each second hardness elastic body includes at least one second elastomer first hardness region and one second elastomer second hardness region, wherein the hardness of the second elastomer first hardness region is less than that of the second elastomer second hardness region; wherein,

[0017] When the second hardness elastic body is subjected to force, the force first acts on the first hardness region of the second elastic body.

[0018] Optionally, each first hardness elastic body includes at least one first hardness region of the first elastic body and one first hardness region of the first elastic body, wherein the hardness of the first hardness region of the first elastic body is less than that of the second hardness region of the first elastic body; wherein,

[0019] When the first hardness elastic body is subjected to force, the force first acts on the first hardness region of the first elastic body.

[0020] Optionally, each of the first hardness elastic bodies comprises a first hardness elastic body first side surface, a first hardness elastic body second side surface, a first hardness elastic body third side surface and a first hardness elastic body fourth side surface, wherein the first hardness elastic body first side surface is arranged opposite to the first hardness elastic body second side surface;

[0021] The third side surface of the first hardness elastic body is arranged opposite to the fourth side surface of the first hardness elastic body;

[0022] The first side surface of the first hardness elastic body contacts the peripheral side wall of the inner gear ring of the inner gear ring;

[0023] The second side surface of the first hardness elastic body contacts the peripheral side wall of the outer gear ring of the outer gear ring;

[0024] The third side surface of the first hardness elastic body contacts the inner teeth of the inner gear ring or contacts the outer teeth of the outer gear ring; wherein,

[0025] The first hardness elastic body is limited at least by the peripheral side wall of the inner gear ring and the peripheral side wall of the outer gear ring.

[0026] Optionally, each of the second hardness elastic bodies comprises a second hardness elastic body first side, a second hardness elastic body second side, a second hardness elastic body third side and a second hardness elastic body fourth side, wherein the second hardness elastic body first side is arranged opposite to the second hardness elastic body second side;

[0027] The third side surface of the second hardness elastic body is arranged opposite to the fourth side surface of the second hardness elastic body;

[0028] The first side surface of the second hardness elastic body contacts the peripheral side wall of the inner gear ring of the inner gear ring;

[0029] The second side surface of the second hardness elastic body contacts the peripheral side wall of the outer gear ring;

[0030] The third side surface of the second hardness elastic body contacts one of the inner teeth of the inner gear ring or the outer teeth of the outer gear ring;

[0031] The fourth side surface of the second hardness elastic body contacts the inner teeth of the inner gear ring or contacts the outer teeth of the outer gear ring; wherein,

[0032] The first elastic body is limited at least by the circumferential side wall of the inner gear ring, the inner teeth, the circumferential side wall of the outer gear ring and the outer teeth.

[0033] Optionally, a plurality of strip grooves are provided on the outer surface of the first hardness elastomer, each strip groove divides the first hardness elastomer into a plurality of elastic regions, wherein the first hardness region of the first elastomer is located in the elastic region in the middle of the first hardness elastomer.

[0034] Optionally, the shape of the inner tooth is: the thickness gradually increases from one end of the inner tooth to the other end, wherein the end with a thicker thickness is the inner tooth thick end, and the other end is the inner tooth thin end;

[0035] The shape of the external tooth is: the thickness gradually increases from one end of the external tooth to the other end, wherein the end with thicker thickness is the thick end of the external tooth, and the other end is the thin end of the external tooth; wherein,

[0036] In the assembled state, the thick end of the inner teeth is arranged opposite to the thin end of the outer teeth, and the thin end of the inner teeth is arranged opposite to the thick end of the outer teeth.

[0037] The present application also provides a design method for a high-elasticity and heavy-load coupling for a mill, and the design method for a high-elasticity and heavy-load coupling for a mill includes:

[0038] Step 1: Obtain the target function;

[0039] Step 2: Obtain parameter information of the high elastic heavy load coupling for the mill;

[0040] Step 3: Create a finite element model of a high-elasticity and heavy-load coupling for a mill according to parameter information of the high-elasticity and heavy-load coupling for a mill;

[0041] Step 4: Solve the finite element model of the high-elasticity heavy-load coupling for the mill using ABAQUS software, and output the hardness information of the first hardness elastic body group and the hardness information of the second hardness elastic body group;

[0042] Step 5: According to the Bayesian optimization method, iterate a new parameter combination and repeat steps 3 and 4 until the number of iterations reaches a preset value;

[0043] Step 6: Obtain the optimal hardness information of the first hardness elastomer group and the hardness information of the second hardness elastomer group according to the objective function and the hardness information of the first hardness elastomer group and the hardness information of the second hardness elastomer group calculated each time.

[0044] The present invention has the following beneficial effects:

[0045] The high-elasticity and heavy-load coupling for a grinding mill proposed in the present invention is designed through the elastomer, so that the first hardness elastomer group and the second hardness elastomer group cooperate to achieve both a softer hardness cushioning property and a harder torque transmission function. When the equipment is started, the elastomer with lower hardness is first subjected to force and compressed, providing a good buffering and shock-absorbing effect; when compressed to a certain amount, the elastomer with higher hardness begins to contact and bear force, thereby transmitting a larger torque. BRIEF DESCRIPTION OF THE DRAWINGS

[0046] Figure 1 This is a schematic cross-sectional structure diagram of a high-elasticity and heavy-duty coupling for a grinding mill in the first embodiment of the present application;

[0047] Figure 2 This is a schematic cross-sectional structure diagram of an inner gear ring of a high-elasticity and heavy-duty coupling for a grinding mill in the first embodiment of the present application;

[0048] Figure 3 This is a schematic structural diagram of an inner gear ring of a high-elasticity and heavy-duty coupling for a grinding mill in the first embodiment of the present application;

[0049] Figure 4 This is a schematic structural diagram of an outer gear ring of a high-elasticity and heavy-duty coupling for a grinding mill in the first embodiment of the present application;

[0050] Figure 5 This is a schematic cross-sectional structure diagram of an outer gear ring of a high-elasticity and heavy-duty coupling for a grinding mill in the first embodiment of the present application;

[0051] Figure 6 This is a schematic structural diagram of an elastic body in a high-elasticity and heavy-load coupling for a grinding mill according to the second embodiment of the present application;

[0052] Figure 7 This is a schematic structural diagram of an elastic body in a high-elasticity and heavy-load coupling for a grinding mill according to the third embodiment of the present application;

[0053] Figure 8 This is a schematic structural diagram of a highly elastic and heavy-load coupling for a grinding mill according to the third embodiment of the present application.

[0054] Legend:

[0055] 1. Inner gear ring; 11. Inner teeth; 2. Outer gear ring; 21. Outer teeth; 3. Elastomer; 31. First hardness portion; 32. Second hardness portion; 12. Peripheral side wall of inner gear ring; 22. Peripheral side wall of outer gear ring; 4. First volume tooth groove; 5. Second volume tooth groove; 111. Thick end of inner teeth; 112. Thin end of inner teeth; 211. Thick end of outer teeth; 212. Thin end of outer teeth; 6. End cover; 7. Strip groove; 311. First hardness area of ​​first elastomer; 312. First hardness area of ​​first elastomer; 313. First side surface of first hardness elastomer; 316. Fourth side surface of first hardness elastomer. DETAILED DESCRIPTION

[0056] The following will be combined with the drawings in the embodiments of the present invention to clearly and completely describe the technical solutions in the embodiments of the present invention. Obviously, the described embodiments are only part of the embodiments of the present invention, not all of the embodiments. Based on the embodiments in the present invention, all other embodiments obtained by ordinary technicians in this field without creative work are within the scope of protection of the present invention. In the description of this application, it should be noted that the terms used here are only for describing specific implementations, and are not intended to limit the exemplary implementations according to the present application. For ease of description, the sizes of the various parts shown in the drawings are not drawn according to the actual proportional relationship. The techniques, methods and devices known to ordinary technicians in the relevant fields may not be discussed in detail, but where appropriate, the techniques, methods and devices should be regarded as part of the authorization specification. In all examples shown and discussed here, any specific value should be interpreted as merely exemplary, not as a limitation. Therefore, other examples of the exemplary embodiments may have different values. It should be noted that similar reference numerals and letters represent similar items in the following drawings, so once an item is defined in one drawing, it does not need to be further discussed in subsequent drawings.

[0057] like Figures 1 to 5 The high elastic heavy load coupling for the mill shown comprises an inner gear ring 1, an outer gear ring 2 and an elastic body group 3, wherein:

[0058] The inner gear ring 1 is provided with inner teeth 11 extending toward the center direction of the inner gear ring 1, and a tooth groove is formed between every two inner teeth;

[0059] The outer gear ring 2 is provided with an outer tooth 21 extending away from the center direction of the outer gear ring. The outer gear ring 2 is sleeved inside the inner gear ring, and one outer tooth is provided in one tooth groove.

[0060] There are multiple elastomer groups 3, one elastomer group 3 is arranged between one of the outer teeth 21 and one of the inner teeth 11, and the elastomer group 3 includes at least a first hardness elastomer group and a second hardness elastomer group, and the hardness of the first hardness elastomer group is greater than the hardness of the second hardness elastomer group; wherein,

[0061] When the high-elasticity and heavy-load coupling for the grinding mill is started, the second hardness elastomer group is first subjected to force. After the second hardness elastomer group is squeezed and deformed to a preset threshold value, the first hardness elastomer group begins to be subjected to force.

[0062] It is understandable that the preset threshold value can be set by changing the hardness and shape of the second hardness elastic body group as needed.

[0063] In this embodiment, the interior of the outer gear ring is used to connect with the shaft of an external device.

[0064] The high-elasticity heavy-load coupling for a grinding mill proposed in the present invention is designed with an elastomer so that the elastomer has both a softer cushioning property and a harder torque transmission function. When the equipment is started, the elastomer with a lower hardness is first subjected to force and compressed, providing a good buffering and shock-absorbing effect; when compressed to a certain amount, the elastomer with a higher hardness begins to contact and be subjected to force, thereby transmitting a larger torque.

[0065] See also Figure 1 In this embodiment, each tooth groove is divided into a first volume tooth groove and a second volume tooth groove by an external tooth 21 located in the tooth groove. The first hardness elastomer group is accommodated in the first volume tooth groove 4, and the second hardness elastomer group is accommodated in the second volume tooth groove 5.

[0066] See also Figure 1 In this embodiment, the inner gear ring 1 further includes an inner gear ring peripheral side wall 12, and the inner teeth are formed by protruding from the inner gear ring peripheral side wall 12 toward the center direction of the inner gear ring;

[0067] The outer gear ring 2 further includes an outer gear ring peripheral side wall 22 , and the outer teeth are formed by protruding from the outer gear ring peripheral side wall 22 toward the outside of the outer gear ring.

[0068] See also Figure 1 In this embodiment, each first hardness elastic body group includes a first hardness elastic body 31;

[0069] Each second hardness elastic body group includes a second hardness elastic body 32; wherein,

[0070] The volume of the second hardness elastic body 32 is larger than that of the first hardness elastic body 31 .

[0071] In this way, it can be ensured that during the movement of the inner teeth and the outer teeth, the force is firstly transmitted to the first hardness elastic body 32 .

[0072] See also Figure 1 In this embodiment, the volume of at least one of the first volume tooth grooves 4 is set to accommodate at least one second hardness elastic body 32. That is to say, in this embodiment, the volume of the first volume tooth groove 4 will be larger than the first hardness elastic body 32 accommodated in the first volume tooth groove 4. In this case, when the outer gear ring rotates clockwise, the second hardness elastic body 32 is squeezed first, and the inner gear ring has not rotated yet, and the outer gear ring rotates. At this time, the gap in the first volume tooth groove 4 is eliminated (that is, the compression amount of the second hardness elastic body 32 is basically equal to the gap in the first volume tooth groove 4). At this time, the first hardness elastic body in the first volume tooth groove 4 begins to be stressed to transmit a larger torque.

[0073] In other words, whether to design a gap, the size of the designed gap and the position of the gap can all be set according to one's own needs.

[0074] In this embodiment, each second hardness elastic body 32 includes at least one second elastic body first hardness region and one second elastic body second hardness region, wherein the hardness of the second elastic body first hardness region is less than that of the second elastic body second hardness region; wherein,

[0075] When the second hardness elastic body is subjected to force, the force first acts on the first hardness region of the second elastic body.

[0076] In this way, the second hardness elastic body can also be given a certain buffering change through different hardness. In this embodiment, the hardness of both the first hardness region of the second elastic body and the second hardness region of the second elastic body is smaller than that of the first hardness elastic body.

[0077] In this embodiment, each first hardness elastic body 31 includes at least one first elastic body first hardness region 311 and one first elastic body second hardness region 312, wherein the hardness of the first elastic body first hardness region 311 is less than that of the first elastic body second hardness region 312; wherein,

[0078] When the first hardness elastic body is subjected to force, the force first acts on the first hardness region of the first elastic body.

[0079] In this way, for the first hardness elastomer, a certain cushioning change can also be given by different hardnesses.

[0080] See also Figure 6 as well as Figure 7 In this embodiment, each first hardness elastic body 31 includes a first hardness elastic body first side surface 313, a first hardness elastic body second side surface, a first hardness elastic body third side surface and a first hardness elastic body fourth side surface 316, wherein the first hardness elastic body first side surface 313 is arranged opposite to the first hardness elastic body second side surface;

[0081] The third side surface of the first hardness elastic body is disposed opposite to the fourth side surface 316 of the first hardness elastic body;

[0082] The first side surface 313 of the first hardness elastic body contacts the inner gear ring peripheral side wall 12 of the inner gear ring 1;

[0083] The second side surface of the first hardness elastic body contacts the peripheral side wall 22 of the outer gear ring 2;

[0084] The third side surface of the first hardness elastic body contacts the inner teeth 11 of the inner gear ring 1 or contacts the outer teeth 21 of the outer gear ring 2; wherein,

[0085] The first hardness elastic body is limited at least by the inner gear ring peripheral side wall 12 and the outer gear ring peripheral side wall 22 .

[0086] In this embodiment, each second hardness elastic body 32 includes a second hardness elastic body first side surface, a second hardness elastic body second side surface, a second hardness elastic body third side surface and a second hardness elastic body fourth side surface, wherein the second hardness elastic body first side surface is arranged opposite to the second hardness elastic body second side surface;

[0087] The third side surface of the second hardness elastic body is arranged opposite to the fourth side surface of the second hardness elastic body;

[0088] The first side surface of the second hardness elastic body contacts the inner gear ring peripheral side wall 12 of the inner gear ring 1;

[0089] The second side surface of the second hardness elastic body contacts the outer gear ring peripheral side wall 22 of the outer gear ring 2;

[0090] The third side surface of the second hardness elastic body contacts one of the inner teeth 11 of the inner gear ring 1 or the outer teeth (21) of the outer gear ring 2;

[0091] The fourth side surface of the second hardness elastic body contacts the inner teeth 11 of the inner gear ring 1 or contacts the outer teeth 21 of the outer gear ring 2; wherein,

[0092] The first elastic body is limited at least by the inner gear ring circumferential side wall 12 , the inner teeth 11 , the outer gear ring circumferential side wall 22 and the outer teeth 21 .

[0093] See also Figure 7 In this embodiment, a plurality of strip grooves 7 are provided on the outer surface of the first hardness elastomer 31, and each strip groove 7 divides the first hardness elastomer 31 into a plurality of elastic regions, wherein the first hardness region of the first elastomer is located in the elastic region in the middle of the first hardness elastomer 31.

[0094] See also Figure 3 as well as Figure 4 In this embodiment, the shape of the inner tooth 11 is: the thickness gradually increases from one end of the inner tooth 11 to the other end, wherein the end with a thicker thickness is the inner tooth thick end 111, and the other end is the inner tooth thin end 112;

[0095] The shape of the external tooth 21 is as follows: the thickness gradually increases from one end of the external tooth 21 to the other end, wherein the end with a thicker thickness is the external tooth thick end 211, and the other end is the external tooth thin end 212;

[0096] In the assembled state, the inner tooth thick end 111 is disposed opposite to the outer tooth thin end 212 , and the inner tooth thin end 112 is disposed opposite to the outer tooth thick end 211 .

[0097] In this embodiment, the high-elasticity and heavy-duty coupling for a grinding mill further comprises an end cover 6 , which is arranged on one side of the outer gear ring 2 .

[0098] In this embodiment, the first elastic body and the second elastic body are made of polyurethane.

[0099] The present application also provides a design method for a high-elasticity and heavy-load coupling for a mill, and the design method for a high-elasticity and heavy-load coupling for a mill includes:

[0100] Step 1: Obtain the target function;

[0101] Step 2: Obtain parameter information of the high elastic heavy load coupling for the mill;

[0102] Step 3: Create a finite element model of a high-elasticity and heavy-load coupling for a mill according to parameter information of the high-elasticity and heavy-load coupling for a mill;

[0103] Step 4: Solve the finite element model of the high-elasticity heavy-load coupling for the mill using ABAQUS software, and output the hardness information of the first hardness elastic body group and the hardness information of the second hardness elastic body group;

[0104] Step 5: According to the Bayesian optimization method, iterate a new parameter combination and repeat steps 3 and 4 until the number of iterations reaches a preset value;

[0105] Step 6: Obtain the optimal hardness information of the first hardness elastomer group and the hardness information of the second hardness elastomer group according to the objective function and the hardness information of the first hardness elastomer group and the hardness information of the second hardness elastomer group calculated each time.

[0106] The design method of the high-elasticity heavy-duty coupling for mills of the present application only needs to input the parameter information of the high-elasticity heavy-duty coupling for mills and the range of geometric parameters and material properties allowed for processing and preparation. The parameters that meet the performance requirements can be automatically iterated within the parameter range. The experimental test iteration process required for the design of the high-elasticity heavy-duty coupling for mills for different application scenarios is reduced. This makes the optimization design method of the present application more efficient.

[0107] In this embodiment, the parameter information of the high elasticity and heavy load coupling for the grinding mill includes:

[0108] Parameter information of the inner gear ring (such as stiffness, size), number information and parameter information (such as stiffness, size) of the inner teeth, parameter information of the outer gear ring (such as stiffness, size), number information and parameter information (such as stiffness, size) of the outer teeth, and initial length of the elastic part.

[0109] In this embodiment, the objective function is as follows:

[0110] in,

[0111] σ max is the maximum torque of the high elastic heavy load coupling for mill in the finite element calculation results, a σ is the weight corresponding to the maximum torque of the high elastic heavy load coupling, y i,Target is the i-th target performance, y i is the i-th performance calculated by the current simulation, a i is the weight of the i-th objective performance.

[0112] In this embodiment, creating a finite element model of a high-elasticity and heavy-load coupling for a mill according to parameter information of the high-elasticity and heavy-load coupling for a mill includes:

[0113] Establish an inner gear ring unit, an outer gear ring unit, and an elastic body unit; wherein the outer gear ring unit and the inner gear ring unit are beam unit models;

[0114] Give material parameters for the inner gear ring unit, the outer gear ring unit, and the elastic body unit respectively;

[0115] The various units are assembled together and their interaction relationships are set to form a finite element model of the high-elasticity and heavy-load coupling for the mill.

[0116] In this embodiment, defining the objective function according to the target performance includes:

[0117] A target property of a given elastic body, such as the stiffness of the elastic body;

[0118] Define the minimization objective function based on the target performance.

[0119]

[0120] Among them, y i,Target is the i-th target performance, y i is the i-th performance calculated by the current simulation, a i is the weight of the i-th objective performance.

[0121] In this embodiment, the interaction relationship of the present application includes the displacement coupling and limiting relationship between the elastic body and the outer gear ring and the inner gear ring.

[0122] Finally, it should be noted that the above is only a preferred embodiment of the present invention and is not intended to limit the present invention. Although the present invention has been described in detail with reference to the aforementioned embodiments, it is still possible for those skilled in the art to modify the technical solutions described in the aforementioned embodiments or to make equivalent substitutions for some of the technical features therein. Any modifications, equivalent substitutions, improvements, etc. made within the spirit and principles of the present invention should be included in the protection scope of the present invention.

Claims

1. A high elastic heavy load coupling for a grinding mill, characterized in that: The high elastic heavy load coupling for the mill comprises: An inner gear ring (1), wherein the inner gear ring (1) is provided with inner teeth (11) extending towards the center direction of the inner gear ring (1), and a tooth groove is formed between every two inner teeth; An outer gear ring (2), the outer gear ring (2) being provided with outer teeth (21) extending in a direction away from the center of the outer gear ring, the outer gear ring (2) being sleeved inside the inner gear ring, and one of the outer teeth being arranged in one tooth groove; An elastomer group (3), wherein the number of the elastomer groups (3) is plural, and one of the elastomer groups (3) is arranged between one of the outer teeth (21) and one of the inner teeth (11), and the elastomer group (3) comprises at least a first hardness elastomer group and a second hardness elastomer group, and the hardness of the first hardness elastomer group is greater than the hardness of the second hardness elastomer group; wherein, When the mill is started with the high-elasticity and heavy-load coupling, the second hardness elastic body group is first subjected to force. After the second hardness elastic body group is squeezed and deformed by the force, the first hardness elastic body group begins to be subjected to force.

2. The high elasticity and heavy load coupling for grinding mill according to claim 1, characterized in that: Each tooth groove is divided into a first volume tooth groove and a second volume tooth groove by the external teeth (21) located in the tooth groove. The first hardness elastic body group is accommodated in the first volume tooth groove, and the second hardness elastic body group is accommodated in the second volume tooth groove.

3. The high elasticity and heavy load coupling for grinding mill according to claim 2, characterized in that: Each of the first hardness elastic body groups includes a first hardness elastic body (31); Each of the second hardness elastic body groups includes a second hardness elastic body (32).

4. The high elasticity and heavy load coupling for grinding mill according to claim 3, characterized in that: Each second hardness elastic body (32) comprises at least one second elastic body first hardness region and one second elastic body second hardness region, wherein the hardness of the second elastic body first hardness region is less than that of the second elastic body second hardness region; wherein, When the second hardness elastic body is subjected to force, the force first acts on the first hardness region of the second elastic body.

5. The high elasticity and heavy load coupling for grinding mill according to claim 3, characterized in that: Each first hardness elastic body (31) comprises at least one first elastic body first hardness region (311) and one first elastic body second hardness region (312), wherein the hardness of the first elastic body first hardness region (311) is smaller than that of the first elastic body second hardness region (312); wherein, When the first hardness elastic body is subjected to force, the force first acts on the first hardness region of the first elastic body.

6. The high elasticity and heavy load coupling for a grinding mill according to any one of claims 1 to 5, characterized in that: Each of the first hardness elastic bodies (31) comprises a first hardness elastic body first side surface (313), a first hardness elastic body second side surface, a first hardness elastic body third side surface and a first hardness elastic body fourth side surface (316), wherein the first hardness elastic body first side surface (313) is arranged opposite to the first hardness elastic body second side surface; The third side surface of the first hardness elastic body is arranged opposite to the fourth side surface (316) of the first hardness elastic body; The first side surface (313) of the first hardness elastic body contacts the inner gear ring peripheral side wall (12) of the inner gear ring (1); The second side surface of the first hardness elastic body contacts the outer gear ring peripheral side wall (22) of the outer gear ring (2); The third side surface of the first hardness elastic body contacts the inner teeth (11) of the inner gear ring (1) or contacts the outer teeth (21) of the outer gear ring (2); wherein, The first hardness elastic body is limited at least by the inner gear ring peripheral side wall (12) and the outer gear ring peripheral side wall (22).

7. The high elasticity and heavy load coupling for a grinding mill according to any one of claims 1 to 5, characterized in that: Each of the second hardness elastic bodies (32) comprises a second hardness elastic body first side, a second hardness elastic body second side, a second hardness elastic body third side and a second hardness elastic body fourth side, wherein the second hardness elastic body first side is arranged opposite to the second hardness elastic body second side; The third side surface of the second hardness elastic body is arranged opposite to the fourth side surface of the second hardness elastic body; The first side surface of the second hardness elastic body contacts the inner gear ring peripheral side wall (12) of the inner gear ring (1); The second side surface of the second hardness elastic body contacts the outer gear ring peripheral side wall (22) of the outer gear ring (2); The third side surface of the second hardness elastic body contacts one of the inner teeth (11) of the inner gear ring (1) or the outer teeth (21) of the outer gear ring (2); The fourth side surface of the second hardness elastic body contacts the other of the inner teeth (11) of the inner gear ring (1) or the outer teeth (21) of the outer gear ring (2); wherein, The first elastic body is limited at least by the inner gear ring circumferential side wall (12), the inner teeth (11), the outer gear ring circumferential side wall (22) and the outer teeth (21).

8. The high elasticity and heavy load coupling for a grinding mill as claimed in claim 6, characterized in that: A plurality of strip-shaped grooves (7) are arranged on the outer surface of the first hardness elastomer (31), and each strip-shaped groove (7) divides the first hardness elastomer (31) into a plurality of elastic regions, wherein the first hardness region of the first elastomer is located in the elastic region in the middle of the first hardness elastomer (31).

9. The high elasticity and heavy load coupling for grinding mill according to claim 1, characterized in that: The shape of the inner tooth (11) is as follows: the thickness gradually increases from one end of the inner tooth (11) to the other end, wherein the end with a thicker thickness is the inner tooth thick end (111), and the other end is the inner tooth thin end (112); The shape of the external tooth (21) is as follows: the thickness gradually increases from one end of the external tooth (21) to the other end, wherein the end with a thicker thickness is the external tooth thick end (211), and the other end is the external tooth thin end (212); wherein, In the assembled state, the inner tooth thick end (111) and the outer tooth thin end (212) are arranged opposite to each other, and the inner tooth thin end (112) and the outer tooth thick end (211) are arranged opposite to each other.

10. A design method for a high-elasticity and heavy-duty coupling for a grinding mill, characterized in that: The design method of the high elastic heavy load coupling for the mill includes: Step 1: Obtain the target function; Step 2: Obtain parameter information of the high elastic heavy load coupling for the mill; Step 3: Create a finite element model of a high-elasticity and heavy-load coupling for a mill according to parameter information of the high-elasticity and heavy-load coupling for a mill; Step 4: Solve the finite element model of the high-elasticity heavy-load coupling for the mill using ABAQUS software, and output the hardness information of the first hardness elastic body group and the hardness information of the second hardness elastic body group; Step 5: According to the Bayesian optimization method, iterate a new parameter combination and repeat steps 3 and 4 until the number of iterations reaches a preset value; Step 6: Obtain the optimal hardness information of the first hardness elastomer group and the hardness information of the second hardness elastomer group according to the objective function and the hardness information of the first hardness elastomer group and the hardness information of the second hardness elastomer group calculated each time.

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